Air-compressor governor.



R. OONRADER.

AIR COMPRESSOR GOVERNOR. APPLleMzos HLBD 001.215.1910. RENEWED 11111112, 1912.

Patented Feb. 18, 1913.

5 SHEETS-SHEET l.

NRADBR.

COMPRESSOR APPLwA'-ON FILED o ,O5399O4f R. CO

AIR GOVERNOR.

GT.26,1910. RENEWBD JULY 12, 1912.

Patented Feb. 18

'.3 SHEETS-SHEET 2.

S 1 we 14 tot R. UNRADER.

AH OMPRESSOR GOVERNOR. APPLicAIxoN FILED @n.261 1910 MNBWBDJULY 12.1912.

pgSgQqc Patented Feb. 18. i913.

ummm! 13a mls R. GONRADER.

AIB COMPRESSOR GOVERNOR.

APPLIOATION FILM) 001126. w10. RBNBWBD JULY 12, 1912` LSo Patented Feb. 18 1913.

R. OONRADER.

AIR COMPRESSOR GOVERNOR.

APPLIGAMON FILED 001.26. 1910. RBNBWBD JULY 12, 1912.

Patented Feb. 18, 1913.

5 SHEETS-SHEET 5.

tio/M1213 RUDOLPH CONRADER, OF ERIE, PENNSYLVANIA.

AIR-COMPRESSOR GOVERNOR.

Specification of Letters Patent.

Patented Feb. 18, 1913.

Application lecl October 26, 1910, Serial No. 589,229. Renewed .Tuly 12., 1912. Serial No. 709,064.

T0 all whom t may concern:

Be it known that'I, RUDoLigH CONRADER, a citizen of the United States', residing at Erie, in the county of Erie and State of Pennsylvania, have invented new and useful Improvements in Air-Compressor Governors, of which the followingis a specification.

This invention relates to air-compressor governors, and consists in certain improvements in the construction thereof as will be hereinafter fully described and pointed out in the claims.

The purpose of the invention is to so control the compressor as toregulate the receiver; pressure. In applicants device,- both the centrifugal governor and a regulator device actuated directly by the receiver pressure are utilized. Governors of this type have heretofore been invented by me, patents for which were issued to me as for instance: #664,468 dated Dec. 25, 1900, #77 5,391 dated Nov. 22, 1904. With these governors, an approximately constant vreceiver pressure is maintained. In the patent to John L. Osborne, July 12,1910, #963,803 a compressor governor is shown purporting to maintain a constant receiver pressure. To illustrate my invention, I show the same construction of pressure lactuating regulating device, feed valve and some other features as are shown in said patent.

The invention is illustrated in the accompanying drawings as follows:

Figure 1 is a side elevation of the combined devices mounted' upon a iuid supply valve casing and showing the balance wheel in section, all of the mechanism being as positioned when the compressor is not running. Fig. 2 -is a vertical longitudinal section of Fig. 1. Fig. 3 is a longitudinal secltion of the shaft mechanism similar to that shown in Fig. 2 illustrating the elements as positioned when the compressor is in'full operation. Fig. 4 is a top view of the mechanism shown in Fig. 1 with the entire shaft and its carried mechanisms removed and showing the pneumatic regulator upon the valve casing top. Fig. 5 is a detail sectional view of the spring pivot mechanism. Fig. 6is an end View of Fig. 7. Fig. 7 is a vertical longitudinal section ofthe pneumatic regulating mechanism. Fig. 8 is a section on the line 8 8 in Figs. l and 2 showing adetail of the centrifugal weights and their mounting and connections. Fig. 9 is a perspective view of the cam collars of the governor. Fig." 10 is a perspective view ofthe cam collars of the governor. Fig; 11 is a perspective view of the main frame portion vof the pneumatic regulator. Fig. 12 shows a section on the line 12-12 in Figs. f and 3. Fig. 13 is a perspective view of the valve lever andits adjustingtoggle connections.

It is to be understood that the compressor' engine is actuated by the iuid received thereby through the fluid supply valve 1 of the usual construction known as a .ported rotary valve. This valve mechanism, plainly shown by the sectional view thereof designated Fig. 2 comprises the T-shell 2 with the inlet port 3 and outlet port 4, having the chamber 5 accommodating the rotatable bowl-shaped valve mem-ber 6, which is` provided with suitable ports 7, which ports are adapted to be brought into and out of registry with the ports 8 of corresponding size in the inner casing 5 of the chamber 5, and thus by rotation of said valve 6 regulating the flow of the vsupplied tiuid through said valve casing. Extending upwardly from said valve 6 is positioned thevalve stern 8 having secured upon the top thereof the actuating arm 10. The valve stern 9 is fixed to the valveby the securing means 11 and passes vertically through the stutiing box 12 provided in the aperture 13 in the circular top plate 19 positioned upon' said T shell 2. Said plate 19 forms the base suppo-rtfo-r the combined mechanisms forming the present invention and has mounted thereon, v`and preferably integral therewith as here shown, the posts20 and 21 positionedupon'opposite sides of said perforation 13, which latter is substantially central of said plate. The radial arm 22 eX- tending inwardly from the post 20 is provided with a bushing member 23 through which 'extends said valve stem 9, while the upper part 24 thereof is provided with said lever 10 constructed integral therewith and also with a base ange 25 having a projecting lug 26 formed thereon and adapted to Contact the pin 27 at the assumptionby the lever 10 of the position at which the uid supply valve 1 is completely closed, said pin being upon the arm 22 and the pin 24 securing the valve stem to said part 24. The toggle connection for operating said valve stem lever 10 is shown in detail in Fig.- 13 and comprises the split nut 28 having the collar 29 journaled thereon and which is easily adjusted upon said eXteriorly-threaded lever arm 10 by the projecting wings 3() and is locked in adjustment by the set nut 31. Said .collar 29 employs the perforated lugs thereof 32 for journaling the pin 33 extending therethrough and pivoting thereto the connecting yoke arm 34 of the toggle, while the opposite end of said arm is pivoted as at 35 to the connecting lever 36 spring pivoted as at 37 to the sleeve 38 for the purpose hereinafter fully set forth.

A governor shaft 39 belted to the main drive or crankshaft of the compressor or its motor, is journaled within the sleeve 40 through which it extends and projects for a suitable distance for receiving the hub 41 of the balance wheel 42 which is secured to the tapered end 43 thereofby the set. nut

4A, while for preventing any possible move-` ment of the shaft longitudinally of the sleeve 40,there is provided the stop ring 45 iiXed to the shaft by the screw pin 46. While lsuch mounting' of the governor shaft directly upon the valve casing is preferred,

other mountings may be used for accommodating the present mechanisms, but in either event the driving belt pulley 47' is secured to said shaft as by the set boltAS. lithin the sleeve 40 said shaft is reduced throughout the central portion 5() thereof for reducing the friction between the same and said sleeve within which it is journaled, said sleeve also having a correspondinglyv enlarged bore portion 5l.

The integral post 20 hereinbefore described has mounted thereon a yoke member 52 secured as by the screw 53 and forming a rigid attachment, while its opposite arms are provided with alining perforations receiving stub shafts 5lV retained therein by the set nuts 55. Said stub shafts 54 extending through the longitudinal slots 56 in the outer casing 38 are received at opposite points wit-hin sockets diametrically positioned in the exterior periphery of the sleeve 40 and at the enlarged or shouldered portion 57 thereof and by which means said shaft 39 is pivoted in the yoke 52 and so supported upon the plate base 19.

The bore of the sleeve 38 having a contracted portion adjacent the inner end thereof provides the shoulder 59 against which is seated the collar 60 surrounding the sleeve 40 while the enlarged portion 57 of said sleeve provides shoulders on the opposite sides thereof for seating one end of the coil spring 61.

The post 21 terminates in a rectangular head 64 having the rectangular opening 65 through which and of less diameter than which, extends the sleeve 66 having a centra] rectangular ridge 67, the extreme front aofiaaofi end 69 ofwhich sleeve enters the sleeve 68, while the outward movement thereof is limited by the pin 68 mounted upon the sleeve 40, 'bot-h end portions of the sleeve being cylindrical.

ln the operative position of the parts as shown in Fig. 3, the inner portion 69 of the sleeve 66 is' so positioned as to slightly compressv the encircling spring 61 by the engagement of the inner end of said sleeve with the movable collar 60, which movement also posit-ions the collar 60 out of engagement with the shoulder 59, during the op eration of the device. The squared middle portion 67 being provided with the front wedge-shaped ridge70, such ridge is received through the rectangular opening and protrudes therefrom, having the remaining upper face of the rectangular ridge 67 flatly contacting the inner face of the head 64.

'llhe governor shaft as here illustrated.

has certain parts thereof arranged designedly for a belt connection between the pulley 47 thereof and a driving shaftpositioned substantially` in vertical relation therewith and belted thereto.

It is to be understood that the present combined governor regulator is essential to t-he perfect operation of the air compressor and that the same is in complete control of the compressor at all times during the o-peration of the latter. This being so. a belted relation between the governor shaft 39 and the'compressor motor or engine is a constant one, excepting in cases of an accidental breaking of the belt connection or the removal of the belt effecting the same.

It is essential that the present devices be in complete control at all times during the operation of the compressor, that there 1s provided the automatic means whereby should an accidental breaking or slipping 0H of the belt communicating with the pulley 47 occur, the air compressor will be at once brought to a dead stop. This result it will be seen is readily accomplished by the mechanisms just described and during which action of the parts their positions are relatively changed from that shown in Fig. 3 to the disclosures thereof in 2. lin such operation the spring 61 acting to expel the sleeve 66 from the receiving sleeve 38 is normally prevented from effecting such an expulsion by the forced retention of the wedge-shaped bridge 70 protruding through the rectangular opening 65 and contacting the inner face of the frame 64 thereof, in which contacting relation said arts are maintained by the normal upward pull of the belt upon the pulley 47 at all times during the operation of the device. Upon a releasing of the belt tension for any reason, the outward exertion of the spring 61 forces the sleeve 66 outward, with the Wedgeshaped ridge 71 sliding within and substanrosato@ tially through the opening'65 of the'head 64. and such koutwar movement being limited by the pin 68 before noted.' The spring 61 being seated upon thev collar normally held out of engagement during the running position with the shoulder 59 is brought into forcible `engagement therewith during the above described outward movement of the parts, s'o that after the contacting of said collar 60 with the shoulder 59 during the outward movement thereof,- an outward movement would also be imparted to the containing sleeve 38, which latter as before noted has pivoted to the underneath side thereof as at 37 the lever 36 effecting communication between said collar 38 and the actuating lever'lO of the fluid supply valve l. The result therefore of the removal of the belt is to trip the retaining sleeve 66 and release the spring 6l whereby the sleeve 38 is moved outwardly and the fluid supply valve l of the compressor motor .completely closed. For this operation the position of the opposite slotted end 7l'of 'the lever 36, as hereinafter fully described is immaterial as such end in this connection aords only the fulcrum point for said lever operated by the application of power at the pivot point 37 upon theactuating sleeve. For'providing a belt connection below or at either side of the shaft, the sleeve 66 may'befrotated as many quarter turns as desired, and then seated as before within the openingl 85.

The centrifugal governor member is as follows: The construction thereof consist' of the fly or balance wheel 42 in the forli' ofan annular lcasing 72 provided with the internally arranged weights 73 .pivoted at diametrically opposite points therein upon the pins 74 positioned through perforations provided in integral projecting lugs 75 carried by the inner periphery of said kcasing These weights -are so pivoted at the perforated ends 76 thereof, that said perforation being designated as 77 inFigs. l and 8, while the outer ends are provided with the pins 78 to which the coil springs 7 9 are attached. The opposite ends of these springs are attached to hooks 80 on the inner portions of said casing. Surrounding the inner hub flange 8l and freely positioned for rotation thereon is the collar 83 forming the four cam faces thereon, saidvcam collar having oppositely projecting ears 86, the ears being connected with the weights by links 88, t-he pins 89'extending through the ears and the link, and the pins 90 through the weights and'links for this purpose as is clearly shown in Fig. 8. The cam collar 95is mounted on lthe hub flange -81'of the balance wheel' and has the cam surfaces 96 which engage the surfaces 85 so that as the collar 82 is rotated the collar 95 is moved axially. The collar 95 is vprol` 'vided wit-h the splinel 94 which eztends into element of the centrifugal governor.

. a groove on the hub to lock the collar against rotation on the hub. rihe annular engaging shoulder 97 on the outer longitudinally movable sleeve 38 is normally in contact with the ca-m collar 95 as clearly shown in Fig. 3, so that the rotary movement of the cam sleeve 82 is through the cam faces communicated to the axial movement in the sleeve 38. This movement being resisted, however, by the spring 62. The spring 62 extends be` tween posts 63 extending upwardly from the sleeve 38- and the end of the adjusting screw 84a, the adjusting screw is .screwed through a post 64. The upper end of the post being split forming the clamp ends 64 which are clamped to the screw 64?. The screw has the squared end 84 by means of which the tension of the spring 62 may be adjusted, and the adjustment may be locked by means of the clamp screw'alp. rThe screw has the extension 84h extending from the spring through t-he posts 68 thus forming a guide for the spring. In this manner, the spring 62 forms a'part of theI centripetal element ofthe governor. rlheV general operation of thesevgoverning weights will be apparent. 'The weights form the centrifugal spring 479 and the spring 62 the centripetal element. The spring 62 it will be noted opposes the outward `movement of the weights through the cam sleeve. With the ordinary speed governor, the 'spring tension should theoretically balance the centrifugal force of the weights at each position. This is known as theoretic tension, and the 'governor as astatic. ln practice, however,-

this is not desirable as the governor would then race and the weights would swing in and out. The speed governor to properly operate, however, should approximate this balancing of forces, and to accomplish it, the centrifugal force should increase as the weights move outwardly 'so `as to maintain approximately the same force as the weights at each position at a constant speed. By observing Fig. 8 it will be noted that-'as the weights swing outwardly, the effective lever arm 'forced by the ears 86 with the axis of the shaft as a center rapidly de creases in length. 'In Fig. 8 I have shown diagrammatically how this decrease in leverage is accomplished. The centers .of the pins 89 and 90 with the weights closed are marked 1L-a., and dash lines connect these points and the positions of the pin 89 with relation to the center. By this arrangement, the effect-ive leverage of the welghts against the spring 62, varies as the weights open and this leverage with the increase 1n spring tension is much more than sufficient to balance the weights at each position provided a constant speed were maintained. The springs 79 have an initial vposition in line withthe pivots lof lit the weights so these also increase in leverage much more rapidly than would be required for an astatic governor. rlFhis is necessary because it is desired to havea much greater normal speed with the weights at their outer position, than at their inner position, commonly several times as great.

The springs, therefore, must not only take care of the increased force due to the outer position of t-he'weights, but must also take care of this desired increase ot speed. By arranging the nut 842I the torce of the spring 62 may be adjusted and consequently the centripetal force easily varied so as to give various normal speeds with each position ot" the weights. rlhe outward impulses edected upon the weights by the centrifugal action results in the longitudinal inward variations of movement of thel sleeve 38, and the return thereof being edected by the spring 62, it is evident thatthe lever 36 is constantly .moved upon its pivotal connection 37 with the sleeve upon all variations in speed of the governor sha-tg-while there is occasioned thereby a consequent partial rotation to the valve stem 9 which obviously results in an opening or closing of the valve 1 for varying the supply ot the actuating fluid to the compressor engine or motor. lin the lever connections through which these operations are eli'ected. it is evident that the operations of the weights upon the tluid valve may be limited by varying the determined length 0f some of said connections through the agency of the positioning of the nut as desired upon the screw threaded valve stem lever 10; it being further noted that the position ot the sleeve 38 is constantly changing when the governor shai't is in motion, thus employing the said end '71 of the level 36 as the tulcrum point, while movementis imparted by said sleeve 36 to said lever at the point of said spring pivot connection 37l therebetween.

The pressure regulator of the governor will now be described. lt is similar to that shown in the Usborne patent heretofore referred to. rlhe main frame work or" this structure as shown separated from all other parts in the perspective view, Fig. 11 is mounted upon the odset 99 ci said post 21 by the bolts or other securing means 100 engaging the bar 101 of said frame work, and which extends at substantially right angles thereto. The main feature ot said :trarne work consists of the pneumatic cylinder 98 having at one end thereof the cross head 102 which has a port opening alining and communicating with said cylinder which port is normally closed by the screw-threaded plug 103. Adjacent said ported end the cylinder is provided 4@with the inlet port 1011 adapted for connection with the pumped compressed air or the storage receptacle therefor and thus communicating the varynoaaaea ing pressure otA the pumped air upon the piston 105y operatively positioned within the cylinder. rEhe aforesaid cylinder is open at its outer end allowing the entrance of the piston rod 106 having a pointed end 107 freely resting within the circular socket 108 `forrned in the outer end of the piston and by which construct-ion the air pressure actuating said piston forces outwardly the piston rod, which latter is in turn pivoted td the arm 109 of the frame through the agency of the angularly bent link 110. The lever 111 adapted to be actuated by said pneumatic means is pivoted upon the pin 112 and within the slotted extension 113 of said arm 109 or" the frame, while said lever 111 further extends through the link 110 and upon the curved inner face 114C of which the roller bearing 115 is adapted to bear, said roller bearing being journaled within the link'110 and uponk the pin' 116 extending through the end of the piston rod. For returning the piston rod and piston inwardly againstthe air pressure and for regulating the force of said return pressure, is provided the spring 117 encircling and forcing outwardly the link 118 pivoted to the lower extremity of said lever 111, while the movable plug 119 furnishes the other abutment for said spring and whereby through the rotation of said plug Within the screw-threaded opening 120 of the cross head 102, the resiliency of said spring is easily adjusted. Said plug is preferably providedv at its outer end with wings 0r eX- tensions 121 for easily turning the same while a set nut 122 retains the member in the desired adjusted position, the ent-rance of the reduced extension 123 of the link 118 within the bore 124 of the plug being evident trom an inspection of the sectional vlew of the structure. lllithin the rectangular alining openings 125 of the fra-me, is slidably-mounted bar,126 with the slot 127 provided through its outer end, in which slotand bearing-upon the sides thereof when being actuated is the rounded or cylindrical upper end 128 of the lever 111. ltivotallymounted upon said slide rod at a point thereon between its supports-is the adjacent end of the lever 36, such pivoting being accomplished by the positioning of the spool 129 within the slot 130 of the lever end 71 heretofore referred to, this spool being sel cured to the slide rod by the screw 131.

From the abovedescriptions will be noted the link and pivot connections between the rotatable valve stem 9 and the slide rod 126 and an actuation of the latter to its fullest extent will obviously result in a complete closing ot the duid inlet valve 1. ln the actuations of said valve by this pneumatic element, the sleeve pivot 37 constitutes the tulcrurn.

By arranging the centripetal element of ment of the pin 131 is to operate the feed valve, and this results in a variation in the engine resulting in a change in speed of the position of the governor weights.- If the centrifugal governor were balanced in the manner of an ordinary centrifugal governor, that is, with the springs forming the centripetal element at practically theoretic.

tension, the centrifugal governor would to the extent of its capacity maintain the speed of the engine constant, thus neutralizing the effect of the fulcrum movement under the inliuence of the pressure device. With the centrifugal governor arranged as here shown, however, with the force of the springs increasing to a pronounced extent above theoretic tension as the weights move outwardly, the change Vin movement of the weights incident to the closing of the valve by the pressure device practically brings into play a dierent governor, the normal speed of which is changed through the change in position of the' centrifugal weight. ln the normal operation ofthe governor under normal conditions, the travel of .the weights from full opening of the valve to full closing is but a small part of the total possible travel of the weights. Thus as the compressor device the lever 36, the weights so .change their position as to form within the limits of normal conditions, a governor device having a normal speed entirely dierent for each position. Thus, with the increase of pressure and a change of the lever 36 so as to primarily close the valve 1, the compressor is slowed down and the weights are drawn in by the centrifugal element by reason of 'this decrease in speed. With each change of position of the fulcrum 131, the feed valve is brought toa complete closure with a diierent position of the governor weight. Thus, as the fulcrum is moved under the influence of the pressure of the pumped fluid, the feed valve is closed with a position of the weights of the governor shaft. When, therefore, the valve is primarily lclosed through the influence of the pressure device, andthe compressor slowed down so that the Weights seek a new position nearer the center of the shaft, they do not vtravel inwardly as far as they would with an ordiclianges the fulcrum ofl nearer the center' nary speed governor because as the weights move inwardly the springs weakenmuch more rapidly than they would if approXit matin'g theoretic tension. Consequently, as the fulcrum 131 moves under the influence of the pumped Huid, the closure-0f the feedv valve is accomplished at a much lower speed lthan with the Ifulcrum 131 at its extreme position under the iniuence of the spring 117 or in the position itassumes in the absence of pressure on the pressure de.l

vice, thegovernor weights having a possible travel vvery much in excess of whatk is required to move the, feed valve from maximum opening to a practical closure. vTn consequence of this, when the fulcrum 131 ischanged, and the weights are brought to a new position, the weights will, in this new position, control the speed at the new position withinthe practical limits of the valve, that is, from full opening to full closure without varying materially this new nor-- mal speed. The 'result of this arrangement is to change the effective force of the centripetal element)` within the power .of the centrifugal element, and thus to change the normal speed of the engine with each position of the pressure device, and the consequence of this is that the governor will lseek that speed between the maximum and mini-` mum which will supply the immediate demand from the receiver, for instance, ifthe maximum speed is 150 revolutions, and the minimum speed is 50 revolutions, and 100 revolutions will satisfy the demand, the governor will nd that intermediate position which lwill give to the engine a speed of revolutions. The pneumatic regulater may be set to operate between any desired limits by the adjustment of the tension adjusting ,means of the piston return spring 117. This controls the npoint at which the piston begins to travel and to thus change the position of the fulcrum 131.

The adjustment 'of the nut 29 ,upon the valve lever 10, it will'be noted, changes the length ofthe lever connections between the pivoted member 36 and said lever, while the changing of the position of such nut upon the lever results in accurately determinin the length of the reciprocatfons of whic the sleeve 33 is capable, under the iniuence' of the centrifugal governing means.

lt will be noted that the lower portion of the curved bearing face 114i ofthe lever 111 is curved abruptly to form an end seat 114" forv the roller bearing '115, so ,as to position the same at its lowest point` ofy movement with .the connected pistonI rod 10S in a substantially vhorizontal plane.

ln connection with the function and operaiis' 114, it will be` seen that the angular fixed positions of the fulcrums of the several different parts are such that considering the pivot 112 of the lever 111 in connection with the pivot 110 of the link 110, both pivots being in the arm 109, and also together with the piston rod pin 106, upon an outward movement of the piston under the inlluenoe of the increased pumped fluid pressure, the distance between the members 116 and 112 is increased and the leverage vantage is enhanced thereby to a corresponding degree while simultaneously therewith the tension of the spring 117 increases.

1n using the pneumatic regulator in conuection with a single acting compressor it is essential that provision bevmade against the complete closing of the fluid supply valve which would possibly result in stalling the compressor on a dead center. rl`his is provided by positioning the adjustable pin 132 within the opening 133 of the cylinder extension 134, which extension also supports the slide rod and is opposed to the head 102; and in further placing upon said slide rod the stop lug 135, which being in a line with the inner free end of the pin 132, is adapted -to engage the same upon its reciprocation with the slide rod 126, and thus the throw of.said rod is limited as desired, said pin being adjustably retained by the set nut 136.

What l claim as new is:

1. ln a pump governor, the combination of a valve controlling the How of motive Huid actuating the pump; of a centrifugal governor member havinga centrifugal element com rising a rotating weight and a centri eta element, said elements being ar range with a pronounced increase in tension over theoretic tension as the weights move outwardly; a pressure device; a connection between centrifugal governor member and the valve; and means actuated by said pressure device and acting on said connection for varying the relative. positions of said member and the valve.

2. ln a pump governor, the combination of a valve controlling the dow of motive duid actuatingthe pump;acentrifugal governor having a centrifugal element comprising a rotating weight and a centripetal element having a ronounced increase in tension over theoretic tension as the weights move outwardly; a pressure device; a connection between the centrifugal governor member and the valve; and means actuated by said pressure device and acting on said connection for varying the relative positions of said member and the valve.

3. ln a pump governor, the combination of a valve controlling the dow of motive fluid actuating the pump; a centrifugal gover'nor member having a centrifugal element comprising a rotating weight and a ceninsane/i tripetal element, the said elements bein@ opposed and arranged to have a pronounced increase in tension over theoretic tension as the weights move outwardly; a pressure device; a connection between the centrifugal governor member and the valve, comprising a lever; and means actuated by said pressure device and acting on the fulcrum of the lever for varying the relative positions of said member and valve.

1l. ln a' pump governor, the combination of a valve controlling the flow of motive fluid actuating the pump; a centrifugal governor member having a centrifugal element comprising a plurality of weights and a centripetal element, comprising a pressureexerting device connected to and operating on both Weights, the device and connection between the device and weights givingl a pronounced increase in tension over theoretic tension as the weights move outwardly; a pressure device;'a valve actuated connection between the centrifugal governor member and the valve; and means actuated by said pressure device and acting upon said valve actuating said connection for varyin04 the relative positions of said member an the valve.

ln a pump governonthe combination of a valve controlling the flow of motive fluid actuated by the pump; a centrifugal governor member having a centrifugal element and a centripetal element, the centripetal element comprising a spring without the plane of the weights, and the centripetal element having a pronounced increase in tension over theoretic tension as the weights move outwardly; a pressure device; a connection between the centrifugal governor member and the valve; and means actuated by said pressure device and acting on said connectionfor varying the relative positions of the said member and the valve.

6. ln a pumpgovernor, the combination of a' valve controlling the flow of motive fluid actuating the pump; a centrifugal governor member having a centrifugal element,

lll@

comprising a rotating weight, and a centripfluid actuating the pump; a centrifugal governor member having a centrifugal element., comprising rotating weights and a cent-ripetal element, the centripetal element comprising links connected to the weights andVV fluid actuating thelpump;a centrifugal gov-- lernor member having a -centrifugal element comprising rotating weights and a centripetal element, the centripetal element comprising an axially moving cam with the axis of the weights as its'center; a rotating cam with the axis of the weights as the center operating upon axially moving cams; a link connection between the rotating cam and the weights, the connection decreasing the leverage ot the rotating cam as the weights move outwardly; a pressure exerting device operating upon the axially moving cam, said device and connection Vgiving a proM nounced increase intension over theoretic tension as the weights move outwardly; a lluid actuated pressure device; a connection between the centrifugal governor and the valve actuating connection; and means ac tuated by said iuid actuated pressure device and acting on said valve actuating con` nection :tor varying the relative positions of said member and the valve et a valve member controlling the dow oi;

motive duid' actuating the pump; a centrifu-A gal governor member having a centriu-I gal element and a centripetal element, said elements being opposed and arranged with a pronounced increase in tension over theo-- retic tension as the weights move outwardly;

means for adjusting one of said elements as to the relative torce exerted thereby; a pressure device; a connection between centrirp-V. ugal governor member and the valve; and

means actuated by said pressure device, and acting on said connection lor varying the relative positions or said member and the' trifugal governor member and the valve;

and means actuated by said pressure device,

and acting on said connection for varying the relative positions of said member and the valve. i

ll. ln a pump governor, the combination of a valve controlling the flow of motive fluid actuating the pump; a centrifugal governor member having a centrifugal element comprising a plurality of weights, and a centripetal element comprising a pressure exerting device connected toand operating on both weights, the device and connection between the device and weights giving a pronounced increase in tension over theo-A retic tension as the weights move outwardly;

means for adjusting t-he pressure exerting device to vary the relative torce of the centrifugal and centripetal elements; a pressure device; a connection between the centrifugal governor member and the valve; and means actuated by the said pressure device and acting on said cornection for varying the relative positions of the said member land the valve,

l2. ln a pump governor, the combination of a valve controlling the dow of motive duid; a centrifugal element comprising a rotating weight; a centripetal element comprising a spring without the plane of the weight; an axially moving cam subjected to the pressure of the spring; a rotating cam operating on the axially moving cam; a connection between the wei hts and the rotatingcam; means for adjusting the tension ot the spring; and a connection for communicating the movement ot the weights through the valve, 9. ln a pump governor, the combinationl i3. ln a pump governor, the combination ot a valve controlling the tlow ol motive duid; a rotating governor weightLA forming the centrifugal element ot the governor; a carrier for said weight; a shaft on which the carrier is mounted; a shaft sleeve form` ing a connection between the weight and the valve; a centripetal element comprising a` spring operating lon said shaft sleeve; an axially' movingy cam moving with said sleeve; a rotatively moving cam operating upon said axially moving cam; a connection between said rotatively moving cam and the weight; a bearing tor the shaft within the shaft sleeve; means for adjusting said spring comprising a screw; and means for locking the screw.

14. ln a combined governor and regulator for air compressors comprising'a lfeed valve for regulating the supply of motive uid to a prime mover for driving the com pressor, a governor shalt; a centrifugal governor weight mounted on the shaft, said weight forming the centrifugal elements ot the governor; a centripetal element operating upon said weight, said elements being opposed and arranged to have a pronounced increase in tension over theoretic tension as the weights move outwardly; and a shift.

able element' mounted on the governor shaftV and actuated with the movement of said weights, said shiftable element being conrected to the feed valve. 4

fl. A combined governor and regulator for air compressors comprising a feed valve for regulating the supply of motive fluid to a prime mover for driving the compressor, a governor shaft; a centrifugal governor weight mounted on the shaft, said weight forming the centrifugal elements of the governor; a centripetal element operating upon said weight, said elements being opposed and arranged to have a pronounced increase in tension over theoretic tension as the weights move outwardly; a shiftable element mounted on the governor shaft and actuated with the movement of said weight; a connection between the shift-able element and the feed valve; and a pressure device actuated by the pumped Huid and acting upo'n said connection to change the relative positions of the shiftable element to the feed valve.

16. A combined governor and regulator "for air compressors comprising a feed valve for regulating the supply of motive Huid to a prime mover for driving the compressor; a governor shaft; governor weights mounted on said shaft and forming the centrifugal element of the governor; a centripetal element operating against the said Weights and having a pronounced increase noaaaoa in tension over theoretic tension as the weights move outwardly; a shiftable element mounted on the governor shaft and actuated with said weights; a connection between said shiftable element; and the feed valve for 4controlling the latter when actuated in one direction by' the governor weights forming the centrifugal element of the governor and a centripetal element, said elements being opposed to each other and arranged to give a pronounced increase in tension over theoretic tension as the weights move outwardly and regulating the motive supply mechanism for the engine controlled by said governor mechanism; a pressure device actuated by the pumped Huid; and an operative connection between said pressure device and the regulating mechanism.

ln testimony whereof l have hereunto set my hand in the presence of two subscribing witnesses.

RUDULPH CONRADER.

Witnesses:

BLANCHE HARTMAN, C. D. llilrenv.

CII 

